Unidirectional, rotary variable delivery fluid pump



Oct. 27, 1953 1.. M. GARNER ET AL UNIDIRECTIONAL, ROTARY VARIABLE DELIVERY FLUID PUMP 5 Sheets-Sheet 1 Filed Sept. 25, 1947 I11 ventons' Lawrence M. Garner Edward .S. McConno/u'e a Attorneys Oct. 27, 1953 L. M. GARNER ET AL 2,656,796

UNIDIRECTIONAL, ROTARY VARIABLE DELIVERY FLUID PUMP Filed Sept. 25, 1947 s Sheets-Sheet 2 III/100$ I11 z'elltors Lawrence M. Garner Edward 5. McGannoh/e WWW BM Oct. 27, 1953 1.. M. GARNER ET AL 2,656,796

UNIDIRECTIONAL, ROTARY VARIABLE DELIVERY FLUID PUMP Filed Sept. 25, 1947 5 Sheets-Sheet 5 Fig. 3.

e i A 1 N m I ,3 v 70 4 1 44% 55 W 3% /3 72 57 32 /V/ v I I I 70 4a 46 86 50 53 60 74 88 Inventors 9/2 Lawrence M. Garner 52 Edward 5. .Mcaonnome L. M. GARNER ET AL Oct. 27, 195.3

UNIDIRECTIONAL, ROTARY VARIABLE DELIVERY FLUID PUMP 5 Sheets-Sheet 4 Filed Sept. 25, 1947 Fig. 6.

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Inventors Lawrence M. Garner Edward S. McConnoh/e @Mm WWW 15m Oct. 27, 1953 L. M. GARNER EIAL 2,656,795

UNIDIRECTIONAL, ROTARY VARIABLEDELIVEIRY FLUID PUMP Filed Sept. 25, 1947 s Sheet s-Sheet 5 4 Fig. 13.

Inventors L awrence M. Garner Edward 5. McConno/n'e By mm Patented Oct. 27, 1953 UNIDIRECTIONAL, ROTARY VARIABLE DELIVERY FLUID PUMP Lawrence M. Gamer and Edward ,S- McConno l Covert, Mich.

Application September 25, 1947, Serial .No- :7 7 6,129

aims. 1

This invention comprises novel and use ul improvements in a hydraulic transmission and more specifically pertains to a unidirectional rotary pump of variable capacity and reversible flow.

This invention relates generally to that type of hydraulic transmission mechanism incorporating therein a fluid motor, or pump, constituting the driving means of the transmission or coupling and a driven motor which... is connected to the driving motor or pump by suitable conduits;

whereby a circulation :of fluid is delivered under the pressure imparted thereto by the driving pump to the driven motor and returned then to the driving pump. In such transmissions, it has heretofore been well "known to vary the speed ratios of the pump and motor by varying the capacity of the former or the latter.

This invention is particularly adapted for use in such a system and it is contemplated that a constant capacity motor, from which power may be employed and taken off in various known methods and ways, shall be actuated at different speed ratios from a driving pump whose capacity may be varied and whose direction of fluid flow may be reversed, by the novel and improved mechanism set forth in this application.

Although the improved variable capacity pump forming the subject of this invention is primarily intended for use in a hydraulic transmission of the character above set forth, it will be readily understood that it is also possessed of'ut-ility and is adapted for use in various other fields and environmentsby reason of its being reversible as to its delivery of fluid and variable in its capacity of fluid delivery, all during a constant speed of rotation in one direction; or alternatively at varying speeds, as desired.

It is a primary purpose of this invention to provide an improved means for varying the capacity of arotary pump while maintaining the speed of rotation of said pump constant and uni-directional.

It is an important purpose of this invention ,to provide a mechanism in accordance with the preceding object wherein the delivery of the pump may be varied from zero to a maximumefor either direction of fluid delivery therefrom.

It is a still further object of this invention to provide a mechanism in accordance with the foregoing objects wherein a novel and improved mechanism is provided for accurately and effectively adjusting the capacity of a pump conform- .ing to the above mentioned object, vand .WhiCh shall be attended by a minimum of wear of the various parts of the apparatus.

These, toge e w th rio s ancilla y objects of the invention which will later become 91134. em as the foll w ng c iption proceeds, are attained by this device, a preferred embodiment of which has been illustrated by way of example only in the accompanyin rawing wherein;

Figure 1 is a perspective view of the pump i u e 2 is a a m n a -y p spe tive view of a po tion o he ope ati g mechan sm o th Pu Parts be g br ken and shown i sections to illustrate certain features of construction;

Fi ure .3 is .a vert cal ongi dinal seetion taken th ou h t e pumps s a o and roto Figure 4 is a h ri n al l n itud na sec iona vi w, taken substa ially upon he sect cn lin 4-4 of Figure 3;

Figure 15 is a transverse vertical sectional view taken substantially upon the section line 5.-..-5 of Figure 3;

Fi ure 6 is a vertical alongitudinalsec iqnal vie taken substantial-1y upon the .se t ne t o :Figure 4.;

Figure 7 is a fra mentary deta led iew u o an enlarged scale taken substantia ly 1 min th :section line 1710f Figure fi Figure 18 is a perspective view of one of the rotor bladesof the invention;

Figure 9 is a lower plan view of one .of the stator :head members of the invention;

Figure 10 is a fragmentary detailed view .taken substantially upon-the section line .I flwzl ll of Fig- -ure9;

Figure 11 is a perspective view of an .element forming a, .part of the invention;

Figure 12 is a perspective view of a further form of rotor blade constituting .the preferred construction thereof in accordance with this in- .vention;

Figure 13 is a vertical longitudinal sectional elevation :through the invention showing thecon- 'struction.ofxthe stator head; and

Figure 14 is a vertical transverse sectional view taken substantially upon the section line 14-44 of Figure 13.

Referrin :now more specifically to the annexed raw n s he ein ik num rals designate similar parts throughout the various views, til-refers gen l y o h versibl and variable deliver pump forming the subject of this invention.

The pump casing includes side plates 12 and .l 4 clamping therebetween a pair of identical upper and lower head and manifold members 1:6 by means of cap screws i8 engaging bores :20 in the ate ribs 48.

head members [6, see Figure 10, or by means of other suitable fastening means. If desired, through bolts might be employed to secure the above mentioned components into a rigid assem bly. The interior of the casing or stator is provided with an annular chamber or recess 22, Figure 6, to receive the rotor assembly.

Upon the side of plate i2 is an outwardly disposed boss 24 provided with an outwardly opening chamber or cavity 26, see Figures 4 and 5, which has a cover plate 28 removably secured by screws 35. Generally rectangular end plates 32 complete the stator casing, being detachably fastened as by screws 34 (Figures 1, 3, i and to the head members It and side plates l2 and I4 by means of bores 36 (Figure 13) The head members I6 are shaped to form fluid inlet and discharge conduits 38 and it, the fiuid fiow therethrough being reversible, as set forth hereinafter.

' adapted to abut the adjacent surfaces of end plates 32 while their inner ends 46 are arcuateiy shaped for a purpose which will presently appear. Adjacent their arcuate surfaces 46, the slides M are provided on opposite sides with lateral, arou- As will be apparent, the slides 44 may move horizontally of the stator chamber between the central casing 22 and the end plates 32.

The sid plates 12 and I4 are provided with aligned bores 58 through which extends a rotary power shaft 52 upon which is rigidly secured, as by keys 54, an annular drum or rotor 55 (Figures 3 and 4) consisting of a hub 55, an annular web 51 and a laterally enlarged annular rim 59, upon which are formed circumferentially spaced, laterally extending, radial notches 58 which slidingly receive U-shaped rotor blades 60, shown in Figures 3, 4 and 12. Each blade is provided with rounded inner and outer edges 62 and 54 respectively, the former being notched at 66 to form bifurcated leg members 68, which extend radially of and in radial slots in the sides of the annular rim 59 and embrace the flange 51 of the rotor 56. The depth of notches 5t and 55 is such that the outer end 64 of the blades may be selectively recessed within the periphery of the rotor and eX- tended into sliding and fluid tight sealing engagement with the inner periphery of the pump chamber in a manner to be now set forth.

Loosely received in the casing chamber 22 are a pair of outer eccentric rings ll! disposed on opposite sides of the above mentioned slides Mi and medially dispos d ribs ll as shown in Figures 9, l0 and 14, on the inner surface of heads is. The outer circumferences of these rings H3 are toothed as at 12 while the inner diameter is circular but eccentrically disposed relative to their outer peripheries. Rotatably journaled in the outer eccentric rings are a pair of inner eccentric rings l'e whose inner circumference is eccentric with respect to its outer periphery. The inner rings are provided with annular grooves 76, on their adjacent surfaces, which are concentric with their inner circumference and slidingly receive the above mentioned ribs or shoulders 33. At diametrically opposite points the outer side surfaces of the rings iii are provided with laterally extending cylindrical bosses or stub shafts l8,

i shown inFigures 2, 6 and '7. r

7 As shown best in Figures 3, 4 and 13, the upper and lower heads iii are spaced from The stub shafts l8 are rotatably journaled by means of eccentric bores 843, Figure 11, in the circular discs 82 which latter are revolubly journaled in bores 84 in the annular discs 85 rotatably received on shaft 52 on opposite sides of rotor hub and rim 55 and 59 and outer and inner eccentrics TB and i4. These discs 85 are provided with circumferential teeth 88 of the same pitch and matching with the teeth 12 of the outer cccentrics.

It can thus be seen by particular reference to Figure i that the annular discs 85 support the inner eccentrics "M which, in turn, carry the outer eccentrics lil, upon the shaft 52. Further, the inner surfaces of discs 85, define with the inner circumferences of eccentric rings 14, the inner surfaces 46 of slides Hi and the inner surfaces of ribs H, a cylindrical pump chamber 90. The arrangement is such that when the gear teeth 12 and 88 are rotated in opposite directions, by a means to be later set forth, the outer circumferences of the outer eccentric rings IE! rotate concentrically with the shaft 52; while the inner circumferences of the outer eccentric rings, and the outer circumferences of the inner eccentric rings, rotatably journaled therein, rotate eccentrically with respect to the main shaft 52 whereby the inner circumferences of the inner eccentrics are moved with a straight line motion in the horizontal plane of the axis of shaft 52, thereby moving the chamber encasing the rotor 55, to vary the eccentricity of the axis of the rotor in said chamber between the limiting positions defined in Figure 6 by the vertical planes a-a and bb. The vertical plane c-c represents a neutral position, at which point the aXis of chamber 96 coincides with the axis of shaft 52 whereby the rotor is centered in said chamber.

To attain the foregoing straight line shifting of the axis of pump chamber 99, the eccentricities of the inner diameters of the inner and outer eccentrics are equal; while the eccentricity of the bore 80 of discs 82 is equal thereto. Thus, rotation of discs 86 by their gear teeth 88, and opposite rotations of the outer eccentrics 10 by their teeth 12 cause rotation by means of discs 82 and stub axles 18 of the inner eccentric rings. This horizontal movement of the inner eccentrics l4 and chamber 90 is accompanied and guided by horizontal displacement of the guiding slides 46 in their guide ways 42 through the inter-engaging ribs and grooves 48 and 16.

For an understanding of the means for adjusting the pump chamber attention is now directed to Figures 2, 4 and 6. A central shaft 92 is journaled as at 94 in the chamber 26 of the boss 24, and provided with a worm gear 96, meshing with oppositely disposed gears 98 and [89 carried by shafts E22 and I64 journaled in the plate l2 and opposite plate [4. The shafts I02 and IE5 extend into transverse bores [fit in the head members, se Figures 13 and 5, and are provided with pairs of identical gears H38 and H6 respectively spaced to constantly mesh with the teeth 88 and '12 of the outer discs and outer eccentrics '50 respectively. Consequently, when the shaft 92 is rotated by any suitable means, not shown, the gears Hi8 and H9 ar rotated at the same speeds in opposite directions, thereby producing the horizontal straight line shifting of the pump chamber components, as above mentioned.

Obviously, any desired position of adjustment between the limiting positions aa and bb may be attained. The efiects of this adjustment are to vary the capacity and delivery of the pump in the following manner.

faces of chamber 90. Consequently as the rotor moves counterclockwise, fluid is carried around the chamber -90 by the blades 60 fromthe inlet 38 and discharged at the outlet 40. Obviously, as the chamber 9|] is moved towards the right, the volume on the left side of the "rotor is reduced While an increased volume is provided on the 1 right which provides a return from the delivery side (or pressure) 40 back to the inlet (or suction) side '38, thereby reducing the effective capacity and delivery of the rotary pump to the passagelo.

When the chamber has reached the position -0 of Figure 6, it will be evident fluid escaping will be equal to fluid carried-around by the blades 6:93 and the delivery or pressure of the pump through the conduit 40 will be zero.

As the chamber 90 is shifted beyond the neutral position c-c and towards the limiting position b-b the volume at the right will exceed that at the left, whereby the rotor, will carry more fluid from 40 to 38 than is delivered around the chamber 90 from 38 to 40 resultin in a reverse flow at the passages, 40 now becoming the suction or inlet side and 38 becoming the pressure or outlet side.

Obviously, for a given speed of rotation of the rotor, the delivery of the pump may be reversed and varied from zero to a maximum for either direction of pump rotation.

It will be observed that the blades establish a fluid tight sealing engagement at their outer curved edges 65 with the inner circumference of the cylindrical pump chamber 9!], bearing against the full width of the chamber upon the inner eccentrics 14, and alternatively upon surfaces 46 of slides 44; while the sides 68 of the blades abut the inner surfaces of disks 86. The annular outer surfaces of rim 59 complete the cylindrical pump chamber.

In order to insure that the outer edges 64 of blades 60 will at all times contact the periphery of chamber 90, a pair of rings H2 which may be serrated on one side to relieve any internal restraining pressure, are loosely positioned on each side of the flange or web 51 between the hub 55 and rim 59 of the rotor. Since the pump chamber 90 is cylindrical, the rings are of sufficient diameter to engage the inner edges 62 of the bifurcated legs 58 of the blades and maintain their outer edges 64 in substantial engagement With the chamber 90. Thus, during turning of the rotor, as the blades on one side move inwardly of the rotor, due to the eccentricity of rotor and chamber, those on the opposite side are moved outwardly by the rings H2. This feature is of value chiefly in starting the pump, in order that all vanes or blades may be in engagement with the chamber wall, since centrifugal force may be relied upon to insure this contact during operation.

Although the form of blade 60 having rounded edges 62 and 64, shown in Figure 12, is regarded as the preferred form, in some instances the modified blade forms of Figure 8 may be found desirable, this form of blade, I I4, having beveled outer edges 8 and with its inner edges curved 6 upon a radius whose locus point is apex of the bevel of the outer edge numerous modifications will readily occur to those skilled this art, after a consideration of the accompanying description and drawings, it not desired to limit the invention to the exact onstruction :shownand described, but all suitable modifications and equivalents may be to, falling within the scope of the appendodolaims.

what is claimed as new, is as follows:

1. A un directional, rotary variable delivery flu-id pump comprising: a stator; a shaft journaled in said stator, a rotor on said shaft, said rotor being provided with a plurality of radially sedans vanes adapted :for impelling a fluid; a

rotor housing defining a pump chamber around said rotor and movable with respect to said stator for varying the capacity of said pump, said rotor housing including a pair of disks concentric with and rotatable with respect to said shaft and disposed on opposite sides of said rotor, and a pair of axially spaced inner rings encirclin said motor and having their inner and outer circumferences eccentric with respect to each other; .said stator having a pair of aligned guide chambers therein communicating with said pump chamber between said rings on diametrically opposite sides of said rotor; slides received in said guide chambers, sa d slides together with said rings, extending the full width of said pump chamber; inter-connecting means between said slides and said inner rings, said means permitting circumferential movement of said inner rings with respect to said slides and preventing radial movement of said inner rings with respect to said slides; means eccentrically journaling said inner rings on said disks and means for selectively rotating said disks and thereby moving said inner rings in a straight line direction parallel with the central axis of said guide chambers; means providing a first fluid passage communicating between the outside and inside of said stator on one side of said guide chambers axis, and means providing another fluid passage communicating between the outside and inside of said stator on the opposite side of said guide chambers axis, movement of said chamber in one direction causing fluid to flow through the chamber and passages in one direction and movement of said chamber in the opposite direction reversing said flow of fluid.

2. The device defined in claim 1 including also: outer rings journaled on each of said inner rings, the inner and outer circumferences of said outer rings being eccentrically disposed with respect to each other, the degree of eccentricity thereof being equal to the eccentricity of the journaling of said inner rings on said disks and said respective eccentricities being oppositely disposed with respect to each other so that rotation of said disks and said outer ring in directions opposite to each other will efiect said straight line movement of said inner rings in a direction parallel with said guide chambers axis and thereby effect movement of said slides along said axis.

3. Means defined in claim 2 wherein the means for selectively rotating said disks comprises: a drive shaft disposed radially of said disks and journaled on said stator; first and second driven shafts journaled on said stator; driving connection between said drive shafts and each of said driven shafts; a first inter-connecting means between said first driven shaft and said disks for rotating the disks in one direction upon rotation of the drive shaft; and a second inter-connectdirection opposite to the directional rotation of said disks upon rotation of said drive shaft.

4. Device defined in claim 2 wherein the means for-selectively rotating said disks comprises: a drive shaft disposed radially of said disks and journaled on said stator; first and second driven shafts journaled on said stator; a driving connection between said drive shaft and each of said driven shafts; said disks having circumferentially spaced teeth on their outer peripheries; a first pair of gears mounted on said first driven shaft engaging the teeth on said disks for rotating the disks in one direction upon rotation of said drive shaft; said outer rings having circumferentially spaced teeth on their outer circumferences; and a second pair of gears mounted on said second driven shaft engaging the teeth on said outer rings for rotation of the outer rings in a direction opposite to the directional rotation of said disks.

5. Device defined in claim 2 wherein the interconnection between said inner rings and said I slides is provided by cooperating grooves and ribs on each thereof.

LAWRENCE M. GARNER. EDWARD S. MCCONNOHIE.

References Cited in the file of this patent UNITED STATES PATENTS Number Name Date 295,704 Wiles Mar. 25, 1884 582,696 Schneible et a1. May 18, 1897 1,338,265 Townsend Apr. 27, 1920 1,467,837 Colebrook Sept. 11, 1923 1,686,532 Ronn ng et a1. Oct. 9, 1928 1,988,213 Ott Jan. 15, 1935 2,287,369 Anderson June 23, 1942 2,312,961 Cowherd Mar. 2, 1943 2,318,292 Chandler May 4, 1943 2,371,922 Saito Mar. 20, 1945 2,451,666 De Lancey Oct. 19, 1948 FOREIGN PATENTS Number Country Date 551,766 France Jan. 13,1923 577,016 Germany May 22, 1933 

